Contouring machine



y 1953 A. c. NORSWORTHY ET AL 2,637, 50

CONTOURING MACHINE l2 Sheets-Sheet 2 Filed May 8, 1950 INVENTORS Arfizur LY Morsu/orly Vl l'lliam B. Ma ya Marion B. fleyff'erf djzger By George L.

ATTORNEY May 12, 1953 A. c. NORSWORTHY El AL CONTOURING MACHINE 12 Sheets-Sheet 3 Filed May 8, 1950 INVENTORS C Norszlorlfi y VWZZz'am 15f Ma 0 ATTORNEY y 2, 1953 A. c. NORSWORTHY ET AL 2,637,950

CONTOURING MACHINE l2 Sheets-Sheet 4 Filed May 8, 1950 1 E0 6 O mmwam w SM a fl rm 8 fi M 13 AWMG A. c. NORSWORTHY ET AL 2,637,950

May 12, 1953 CONTOURING MACHINE Filed May 8, 1950 12 Sheets-Sheet 6 WW Z;

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V 0 f w m m A W SMM flflL r m n mw my rm? AWMG lllllllL NNN y 1953 A. c. NORSWORTHY Ei- AL 2,637,950

CONTOURING MACHINE Filed May 8, 1950 12 Sheets-Sheet s William B M 0 64% Alambn B fierz BY J 09% we digger ATTORNEY w 1193 A. c. NORSWORTHY ET AL 2,637,956)

' CONTOURING MACHINE Filed May 8, 1950 12 Sheets-Sheet l0 INVENTORS Arfhur C lVorsu/o'rfQ Vl jllz'am -B M yo 214225022 3 Sgqfferf ATTORNEY May 2 11953 Filed May 8, 1950 l2 Sheets-Sheet 11 I vii/7110 Marion B. Se gfferf BY Gea ge L. yer

ATTORNEY S R O T N E V m 12 Sheets-Sheet 12 Art izr C, Norszwrf/z 14 27/2277 5. Mayo Mar/022 5. Se fferz May 12.3, 11%;? A. c. NORSWORTHY ET AL CONTOURING MACHINE Filed May 8, 1950 ATTORNEY Patented May 12, 1953 GQ 'OU AQHI'N Mo h-w G- 'Nqrsmqri Bhq b s me e L- ding'er amp o am B} Mam'fl tm i a e nd Meiien fie t, mpt n Ye ains? to 'i z ih'l a Ser i Qetmxaii y Newport News, Va a corporation of Virginia A pligaiigl} g, 1950, Se,ria N 160, 1

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A suitable bearing 32 is likewise mounted upon the base 26. Rotatably carried through the bearing 32 is a torque shaft 33, which is provided with a pair of keys 33' extending longitudinally on each thereof, as shown in both Figs. 1 and 2. Slidably carried upon the torque shaft 33 is a follower arm 34.

The follower arm 34 is keyed to the torque shaft 33 by means of a clamp 35 which slidably fits around the keys 33'. As shown in Fig. 2, the follower arm 34 preferably is provided with an interchangeable head 34. The interchangeable heads vary in length and are for use when different types of work are in the machine. By using heads 34' of different lengths the effective overall length of the follower arm 34 may be changed as desired.

Mounted upon the upright end of the follower arm 34 is a bearing 36 into which a shaft 31 of a follower wheel 38 freely rotates. The follower wheel 38 rotatably bears against the template 3| during the operation of the machine. As will be seen from a study of Fig. 2, the follower arm 34 is moved about an axis which is the center of torque shaft 33, as directed by the contour of the template 3| as it rotates. This motion in turn is translated to the torque shaft 33.

An arm 39 is pivotally connected to the end of the torque shaft 33 and lies outside of the bearing 32. The arm 39 is adapted to receive a sliding counterweight (not shown) which may be used, if desired, to hold the follower wheel 38 against the template 3|.

A threaded drive screw 48 extends through the follower arm 34, as shown in Fig. 2, and

threadably engages a nut 4| provided therein. Rotation of the threaded drive screw 40 moves the follower arm 34 longitudinally the length of the shaft 33, which in turn moves the fo lower wheel longitudinally against the. template 3|. This particular function of the machine will be explained more in detail in connection with the explanation of the entire machine.

The torque shaft 33 is supported at the end opposite the bearing 32 by means of a pair of bearings 44, each mounted upon the base 26. In between the bearings 44 and the bearing 32 is a pair of support members 45 securely mounted upon the torque shaft 33 adjacent either end thereof. Each of the support members 45 is provided with a connecting collar 46, shown in detail in Fig. 15, he d to the torque shaft 33 by means of stud bolts 41. Securely attached to the connecting collar 46 is a sub-extension 49 of the torque shaft 33, which is rotatably mounted in bearings 44, as shown in Figs. 1 and 15. The threaded drive screw 46 is rotatably supported at each end in each of the members 45 by means of a friction bearing 49, and the support is securely but adjustably fastened to the torque shaft 33 by means of stud bolts 50.

If desired, a conventional rotation counter 42 may be connected to the end of the threaded feed screw 40 and mounted on the support member 45 adjacent the bearing 32, as shown in Fig. 2.

Upon one end of the sub-extension 48 of the torque shaft 33 is a crank arm 5|, as shown in Figs. 1 and 19. Suitably secured to the crank arm 5| by means of a crank pin 52 is a connecting rod 53, which is provided, intermediate its ends, with an adjusting means 54, here shown to be conventional adjustable lock nut arrangement.

The other end of the connecting rod 53 is connected to a second crank pin 55, best shown in Figs. 1, 6 and 19. The crank pin 55 is carried upon a lug or bracket 56 in the form of a projecting arm formed integral with or attached to a connecting member 51. The connecting member 51 is attached at both ends to pivoted bearing support plates 58 and 59.

The bearing support plates 53 and 59 are pivotally mounted upon a shaft 60, as best shown in Fig. 6, which in turn is supported upon a mounting 6| and housing 62. The shaft 60 is secured to the housing 62 by means of a nut 63 threaded thereon. The mounting 6| and housing 62 are carried upon a supporting plate 64. Collars 65 carried upon the shaft 60 retain the plates 58 and 59 in spaced relation from the mounting 6|. The shaft 69 extends through the mounting 6| and is provided with an enlarged extension 66, as shown in Fig. 6. The enlarged extension 66 has provided therein a friction bearing 61 which rotatably carries a shaft 68.

The shaft 68 extends through and is supported intermediate its ends by a second bearing 69. Keyed upon, or otherwise securely fastened to the shaft 68, intermed ate the mounting 6| and. bearing 69 is a V-belt pulley or sheave 10. While the sheave 10 is shown here constructed to receive three V-belts 1|, it is to be understood that any number of belts may be provided suitable for the type of load. A spacer 12 is provided on the shaft 68 and retains the sheave 19 in its axial position from the bearing 69.

Upon the extreme end of the shaft 68, extendng through the bearing 69, is mounted a second V-belt pulley or sheave 13, which is here shown as receiving two V-belts 14, but again it is to be understood that such number of belts may be utilized as desired. The pulley 13 may be locked to the shaft 68 in any way desired, but is here shown as locked by means of a suitable key and set screw.

An electric motor 15 is suitablymounted upon the base 26 and carries a V-belt pulley or sheave 16, which drives V-belts 11. The bolt 15 adjustably ties the motor 15 to the base 26. The belts 11 drive a V-belt pulley 18 mounted upon a shaft 18'. The shaft 18 is rotatably mounted upon a pair of bearings 19. Another V-belt pulley is also mounted on the shaft 18' and together with the pulley 18 is keyed thereto. The V-belts 14 are driven by the pulley 80, and the drive assembly just described provides a speed reduction drive between the motor 15 and the shaft 68.

The V-belts 1| drive a V-belt pulley or sheave 8|, which in turn is securely affixed to a shaft 82. The shaft 82 is provided on one end with threads 83, as shown in Fig. 6. Hold to the shaft 82 by means of a nut 84 is a flywheel 85. Intermediate the ends of the shaft 62 there is provided a bearing hanger or support 86 mounted upon the pivoted bearing plate 58. Provided in the end of the hanger 86 is a friction hearing 81, which rotatably supports'thc shaft 82,.

A detachable coupling 82' attaches" the. shaft.

82 to a cutter head drive shaft 88. The cutter head drive shaft 88 adjacent'the' end nearest the coupling 82 is" supported by" means of a suitable bearing 89, here shown as a friction bearing, provided in the bearing support plate 58. A thrust bearing spacer 891" may", if desired,

be provided on the bearing 89 to bear against the coupling 82'.

A cutter 98 provided with milling teeth BI, as shown in detail in Fig. '7, is attached to a shaft 92 by means of a stud bolt 93, or the like. The shaft 92 is rotatably mounted in a friction bearing 34, which in turn is suitably mounted in the bearing support plate 59. The shaft 92 is detachably connected to the cutter shaft Silby means of a pin 95.

It will be seen from the foregoing detailed description that the cutter 90 will be rotatably i driven from the V-beltpulley or sheave 7'3 but at the same time is permitted to swing freely about an axis, the center of which is coincident with the center of shaft Ill]; and that shaft 50, pivotally supporting plates 5t and 55, which in turn are attached to connecting rod 53, allows the cutter 90', while it is rotating about its own axis, to swing or pivot about the axisof the shaft 60. In other words, when the follower wheel 38 bearing again-st the template in causes the follower arm 34 to pivot the torque shaft 3%, the crank arm 5 I actuating the connecting rod 53' causes the cutter fill to: pivot about the axisof the shaft 6-9.

By way of illustration, Fig. 1-9 has been prozqi' vided with schematic lines representing a paral lelogram. A line is drawn through the center line of the machine A-A, the center of shaft 60, and thence through the center of shaft til which is also a continuation of the center of shaft 33.

The second line of the parallelogram is the center of the link 53 with the line passing through the center of pins 52 and 55. Regardless of the operation of the machine, these lines are always parallel. shaft to and pin 55 is always parallel to a line drawn through the center of shaft 43 and pin 52. The distance between the center of shafts 6i) and G8 is represented by Y, and between the center of pins 56 and 52 by Y". Y and Y may or may not be equal, but remain constant at all times.

There is a direct ratio between the distance between the center of the shafts 60 and 88 and the effective length of the follower arm tli'from the center of bearing 3-6 and the center of shaft 33. In the drawings this ratio is 6:1. Schematb cally indicated in Fig. 2, the line representing the distance between the centers of shafts 33 and 31, is equal to six times the distance between the centers of shafts 6.9 and .88; If diiierent support plates 518 and 5:?! are used, it is necessary to change to head "34' of the iollower arm 3d. While a ratio or 6:1 is here shown, it is to he understood that other ratios may be for ditierent types of work.

A second housing I041, identical :to the housing 62, is :also mounted upon the support plate 64. Both of the housings 6.2 and I-B I are provided with friction bearings I02 and I53, respectively. The bearings I02 and H83 may be split, as best shown in Fig. 8. Rotata bly mounted within the bearings Hi2 and I-M, and supported adjacent its extremities thereby, is a barrel 105. The barrel "5 is provided with journals W6 receive A line drawn through the center of (iii the bearings m2 and 10.3. 'Ihrustbea ms plates- IB! are rovided, as shown in Figs. 6 andfi The barrel I05,v as shown, is tubular and. fi e era'bly should be fitted to thefriction bearin s.

and. IE3 to the absolute. minimum clearance.

A. drive assembly. designated generally by the numeral I08, and shown in detail in: Fig. 8, is.

provided on one end. of the barrel. I05. The drive assembly I08; consists. oi an annular plate I019! having a shoulder III! which fits into the barrel in friction contact with the. bore thereof. A sprocket wheel III is mounted against the plate. Hi9- and is held thereagainst. between plate Iflil and a second plate IIZ. A template mounting plate H3 is positioned adjacent the plate H2. Stud bolts H4 pass: through the annular plate I09, the sprocket wheel I I I, plate I 12 and mounting plate. II 3. of drive assembly I98, and are threaded into the barrel I05. When the stud bolts I M are tightened, the whole assembly is securely affixed to and rotates with the barrel. H35. Securely mounted upon the template mounting plate II'3 there may, if. desired, be provided a template support I15. The template 3|, as best shown in Fig. 2, is secured to the support H5 in any desired manner, as by bolts, screws or the like (not shown). The support H5 is attached to the template mounting plate I I3, as by bolts, screws, or the like.

Turning now to a detailed description of the structure of thebarrel, attention is directed to Figs. 1, 6 and 8 to 14 inclusive. A chuck holding plate I It is secured to the end of the barrel I165 opposite the drive assembly I08 by means of stud bolts II-"I spaced circumterentially thereabout. A shoulder IIB, provided on the plate I Iii as shown in Fig. 6, is in friction engagement within the inner circumference of the barrel Hit. The chuck holding plate I it is provided with an. annular recess H9 into which are provided a pair oi chuck jaws 12E. The chuck jaws I20, as best shown in Figs. 6, 8 and 11, are held in adjustable position in the recess H9 by means of four sets of Allen set screws Ill. The chuck jaws 520 may be of any desired type but preferably should be of complementary inner faces and receive thenebetween in slidable engagement blank stock or work piece I22. As will be seen. from a study of Fig. c, the chuck jaws I20 are positioned adjacent to, but spaced apart very slightly from, the cutter 90, and the finished blade IE3 is milled, out, or ground, at this point.

A pair of rods i2kl extend the length of the inside barrel I i5 and are securely supported at either of their ends within the plates and HS, as best Shown in Fig. .8,

The rods IN- preferably should be highly polishecl and are adapted to slidably receive thereon a blank stock pusher assembly I25.

The blank stool; pusher assembly 425 consists oil a pin I25 which abuts against the end of the blank stock I22. I26 is formed integral. with extends from a reduced shoulder -I2'I, provided upon the end of a bearing member M28. The bearing member I28 is provided with a flange I29, as best shown 13. A pair of arms I33 having a pair of aligned holes IitI is provided on the end oi member I28 opposite the pin. I25, as shown.

The hearing member I28 is slidably fitted into across piece 532, with the reduced shoulder 52-"; extending therethrough. At both ends of the cross piece I 32 there are provided a pair of holes 433 which .slidab'ly receive each one of the pair Qfrods .IM. The flange I2!) is inserted into a recess I34 formed intermediate the ends of'the' cross piece I32, as shown in Fig. 13.

A second retaining member I35, in the form of an I, is provided with a hole I36 which receives a second collar I31 formed on the bearing member I28 adjacent the shoulder I29. The second retaining member I is provided with a pair of flanges I38 extending at right angles to the main portion of the retainingmember I35. Aligned holes I38 formed in the flanges I38 coincide with complementary holes I39 formed in the cross piece I32 and the flanges I38 embrace the cross piece, as shown in Fig. 13. The retaining member I35 is attached to the cross piece I32 by means of bolts I40. The retaining member I35 serves to hold the flange I29, and consequently the bearing I28, in the recess I34 of the cross piece I32. The flanges I38, on the opposite side of the retaining member I35, are provided witha pair of aligned rectangular recesses I42.

.A pushing bar I43 is located in the aligned recesses I42, as shown in Fig. 14, and is provided with a hole I44 which is aligned with the holes I3I of the bearing I28 and is pivotally connected to the member I28 by means of a pin I45.

On each end of the pusher bar I43 there is provided a rotatable wheel I46. The wheels I46 are retained on the pusher bar I43 by means of nuts I41. It is to be here understood that while the wheels I46 are shown to bear frictionally on shafts I48, integrallyformed on the pusher bar I43, any form of bearing may be used; and, if desired, a roller bearing assembly may be substituted for the friction bearing.

The barrel I05 is provided with a pair of elongated openings I50 spaced 180 apart and extending substantially the length of the barrel between the plates I09 and I I6, as shown in Figs. 8, 12, 13 and 14. The pushing bar I43, as best shown in Figs. 12 and 13, extends through the openings I50 in the barrel I 05, and the wheels I46, as shown in Fig. 13, are located externally of the barrel.

Surrounding the barrel I05 is an annular ring I5I, which is spaced apart from the barrel I05, as best shown'in Figs. 8, 12, 13 and 14. Pivotally mounted upon the annular ring I5I and disposed 180 apart is a pair of identical split clamps I52. The clamps I52, shown in detail in Figs. 9 and I0, consist of a pairof identical jaws I53, each provided with a segment of a threaded nut' I54,

which are held in jaw I53 by means of screws I55. Each of the jaws I53 is provided at one end thereof with a hole I56 through which a stud bolt I51 passes and threads into the ring I5I to pivotally connect each jaw I53 of the clamps I52 to the annular ring I5I. Through each of'the jaws I53, opposite the hole I56, there is provided a hole I58, which extends therethrough for the purpose of receiving a bolt I59, which may be provided with wings I60, if desired. The bolt I59 may be provided with a nut (not shown) or one of the holes I58 may be threaded, as shown in Figs. 10 and 14, to receive the complementary threads of the bolt I59.

The jaws I53, when closed, embrace a pair of threaded feed screws I6I located 180 apart, as best shown in Fig. 13. It is to be here observed that this particular construction of the clamp and threaded drive screw is to permit the clamps I52 to be located in threaded engagement with the screws I BI when the machine is in operation, and to be quickly disengaged therefrom by opening the jaws I53 when new work is placed in the barrel, and the annular ring I5I, together with the pushing bar I43 and its assembly, is returned to the end of the barrel away from the cutter 90.

The threaded feed screws I6I are rotatably supported in friction bearings I62 mounted in suitable brackets, or the like, formed integral with or attached to the cases I04 carried on the mounting 62. Nuts I63 are provided on the ends of the threaded drive screws, as shown in Fig. 13, to retain these screws in place.

The opposite ends of the threaded drive screws I6I are rotatably supported within bushings I64 suitably mounted in brackets or the like I65, formed integral with or otherwise rigidly attached to the case I04, supported by the mounting IOI. A thrust bearing plate I66 is provided between the threads on rods NH and the bearings I64.

Briefly, the operation of the barrel is described as follows:

During the operation of the machine, the barrel is rotated in the bearings I02 and I03 by means of a driving chain I61 carried upon the sprocket wheel III. The particular drive means for the chain I61 will be described in detail later in conjunction with the operation of another section of this machine. It is to be here emphasized that the barrel I05 rotates about the same axis with the template 3 I.

While the barrel is rotating about its axis, the rods I24 will carry the blank stock pusher assembly I25 with the barrel, and this in turn will rotate the pushing bar I43. This movement in turn causes the wheels I46 to roll about the face I5I of the annular ring I5I. The threaded feed screws I 6I are rotated by means of a driving mechanism which will be described in detail later. As the threaded drive screws I6I turn, the clamps I52 cause the annular ring I5I to move towards the work piece I22, and to push against the wheels I46 as they rotate with the barrel; this forces the pin member I28 into a hole (not shown) provided in one end of the work piece I22, which in turn is caused to slide through the jaws I20 at the same time the barrel rotates the work piece. This action progressively addresses the work piece I22 against the cutter 90.

Each of the threaded feed screws I6I is provided with a reduced section I68 on the end thereof, adjacent the friction bearing I64. An annular collar or coupling I69-is attached to the reduced section I68 of each of the feed screws I6I by means of a pin I10. The collar I69 is also provided with a reduced section I1I which in turn is connected to a small sprocket wheel I12 by means of a pin I13. Each sprocket wheel I12, is provided with a drive chain designated I14 and I15, respectively, as shown in Fig. 4.

Attention is now directed to Fig. 4 for a detailed explanation of the driving mechanism operating chains I61, I14 and I15. The supporting plate 64 serves as a cover for a motor and gear box housing, designated generally by the numeral I16. The housing I16 is provided with an end plate I 11. An idler sprocket I18 is suitably bolted to the end plate I11, as shown, and preferably is provided with a suitable adjusting means for taking up the slack in driving chain I15.

Also located upon the end plate I11 is a dual idler sprocket I19 which is suitably mounted on the end plate I11 by means of bolts or the like. One of the dual sprockets I19 receives drive chain I14, and the other sprocket receives a drive chain I80. It might be well to explain here that the purpose of the dual idler sprocket I19 is to enable the driving of chain I14, connected to drive 11 to slide longitudinally within the tubular member 2453, but by means of the keys 241 the shaft 242 causes the tubular member 243 to rotate.

A second universal joint, designated generally by the numeral 258, and also of conventional design, is provided on the end of the tubular member 243 opposite the coupling, as shown in Fig. 15. The opposite end of the universal joint 258 is connected to the threaded feed screw 48, as shown. The universal joints and connections of the above-described assembly may be made by welding or the like, or, if preferred, may be provided with pins or threads.

Attention is now directed to Fig. 3, in which there is shown a conventional lubrication or coolant system provided in the sub-base 25 and located beneath the cutter head. This coolant system is provided to remove the cuttings from the cutter 88 and to hold down the temperature of the metal as it is milled or cut or ground. The

tank 253, strains or filters out the cuttings in the tank and permits the return of the coolant into a coolant tank 255, where the coolant is again strained by means of a second strainer The coolant is then picked up by means of a pump 251 and is directed in a stream against the work piece and the cutter or grinding wheel by means of a nozzle (not shown). It is to be understood that the coolant system forms no part of this invention and is of conventional design.

When it is desired to convert this machine from a cutting or milling machine to a grinding and finishing machine, it is necessary that a grinding wheel 288 be substituted for the milling tool or cutter 88, as shown in Fig. 18. Inasmuch as extreme accuracy is desired in grinding the finished product, it is necessary to continually dress the grinding wheel 268. As the grinding wheel is dressed down, suitable arrangement must be made for reducing the effective diameter of the follower wheel 38. The arrangement for accomplishing this, as shown in Fig. 18, is described in detail as follows:

A dressing wheel 26 I, which may be of any conventional design, is shown supported by a yoke I 262, which is mounted upon a plate 263 carried upon the pivoted bearing support plate 58. A

threaded member or connecting rod 264 is attached at one end to the yoke 262 and is threaded into a collar 285 rotatably mounted on the plate A suitable ratchet mechanism for rotation of the collar 265 is provided and is designated generally by the numeral 266. The collar 265 is affixed to a ratchet wheel 268. A pawl 288, pivoted to the plate 263 in any suitable manner, as shown The control 212, simultaneously with operating.

' solenoid 21!, operates a second solenoid 213. The

second solenoid 213 in turn actuates a connecting arm 214, connected to a pawl 215 pivotally mounted upon a plate 216 in any suitable manner. The plate 216 is mounted upon the follower arm 34 in any desired manner. The pawl 215 actuates a ratchet wheel 211, which in turn rotates a threaded collar 211 similar to the collar 265. The collar 211 in turn actuates a screw member 218 upon which there is securely mounted a bearing 219.

Rotatably mounted upon the bearing 218 is a wheel 288. The wheel 288, preferably, should be mounted on the bearing 219 by ball or roller bearings, but it is here to be understood that friction bearings may be used, if desired.

The wheel 288 cooperates with a cylindrical drum 28l in which there is provided a central opening 282 in the form of a truncated cone, as

shown in Fig. 18. The inner surface of the truncated cone 282 is contacted by the surface of the wheel 288. As the wheel 288 is moved by the threaded screw 218, it is caused to mov from side to side of the cylindrical drum 28! with the Wheel 288 contacting the inner surface of the cylinder 28I at different points along its inner periphery.

The outer circumference of the cylindrical drum 28! is provided with a follower wheel 283, which is substituted for the conventional follower wheel 38. The cylindrical drum 281 is held in place between plate 216 and a second plate 284 and is permitted to rotat freely between these plates by means of suitable bearings 285, which may be of the friction type or, if desired, may be provided with small balls or the like (not shown).

It will be seen from examining Fig. 18 that such an arrangement will constantly change the effective radius of contact between the wheel 288 and the cylinder 28!. The effective radius of the follower wheel is thereby changed as the wheel 288 moves longitudinally. By effective radius is meant the distance from the point on the circumference of wheel 283 touching the template to the center of shaft 218. Regarding the device from right to left as viewed in Fig. 18, when the wheel 288 is moved to th right the effective radius of wheel 283 is decreased, and conversely, when the wheel 288 is moved to the left the effective radius of the wheel 283 is increased.

It will be seen from the foregoing description that as the dressing wheel 26l moves downward with the cutting away of the grinding wheel 268 by means of the timed control 212, the wheel 288 will be moved along the inner periphery of the truncated cone opening 282, and'the effective diameter of the follower wheel 283 will be changed in direct ratio with the actual diameter of the grinding wheel 260. Thus, even though the grinding wheel 268 is cut down constantly, the same ratio between the follower wheel 283 and the grinding wheel 268 will always be maintained.

While the operation of this machine has been explained in detail as the various assembled parts have been referred to, a. general brief overall summary of the operation of this machine will be given here.

Basically, the fundamental operation of the machine is the provision of a rotating template 3| turning about the same axis as that of the work piece I22, and the provision of a direct reduced ratio, here specifically designated as 6:1, in order to reduce inaccuracies of the template 3|. The work piece, first having been inserted tially the length 15 turning all of the feed screws in timed relation whereby the blank stock is moved longitudinally of the feed barrel as the follower moves longitudinally of the template.

3. A contouring machine comprising a base, means to rotatably mount a template on said base, a blank stock feed barrel, means rotatably mounting said feed barrel on said base, means for rotating the blank stock feed barrel with the template, a pair of rotary feed screws mounted on said base and extending longitudinally of said feed barrel, means carried by said feed screws for moving a blank stock longitudinally of said feed barrel, a follower for the template, a torque shaft rotatably mounted on said base,

said follower being slidably mounted on said torque shaft, a second rotary feed screw, means pivotally mounting said feed screw for rotation about the torque shaft, said last mentioned feed screw being threadably connected to said follower for longitudinally moving said follower the rotary cutter head pivotally mounted on said base, and linkage means connecting the cutter head to the torque shaft for moving the cutter head in a pattern similar to that of the template.

4. A contouring machine comprising a base,

a rotary cutter, means pivotally mounting said cutter on said base, means to rotatably mount a template on said base, a blank stock feed barrel, means rotatably mounting said feed barrel on said base and adapted to rotate with said template, blank stock feeding means carried by said feed barrel, a torque shaft rotatably mounted on said base, a follower arm slidably mounted on said torque shaft, a follower wheel rotatably carried upon said follower arm, plates mounted upon said torque shaft adjacent the ends thereof, a threaded drive screw rotatably mounted in said plates, said drive screw being threaded through said follower arm for causing said arm to slide longitudinally of .said torque shaft, a universal joint connecting said threaded drive screw to a driving means, and a linkage connecting said torque shaft to said rotary cutter for pivoting said cutter in a pattern similar to said template.

5. A contouring machine comprising a feed barrel having elongated slots extending substanthereof, bearings rotatably mounting said feed barrel on said base, chuck jaws mounted in said feed barrel adapted to slidably receive a blank stock therebetween.

blank stock feeding means slidably mounted within said feed barrel, said feeding means extending through said elongated slots, an annular ring surrounding said feed barrel positioned to engage the feeding means extending through the slots in said feed barrel, and rotary feed screws mounting the annular ring upon said base, said feed screws being in threaded engagement with said annular ring for movement thereof longitudinally of said feed barrel.

6. A contouring machine comprising a feed barrel having elongated slots extending substantially the length thereof, bearings rotatably mounting said feed barrel on said base, chuck jaws mounted in said feed barrel adapted to slidl6 ably receive a .blank stock therebetween, blank stock feeding means slidably mounted within said feed barrel, said feeding means comprising a pair of aligned rods mounted longitudinally within said feed barrel, a cross piece slidably mounted on said rods, a pushing pin pivotally mounted on said cross piece adapted to engage the blank stock and push the same through the chuck jaws as the feed barrel rotates, a transverse arm pivotally mounted on said cross piece, said transverse arm extending through the elongated slots in said feed barrel, an annular ring surrounding said feed barrel positioned to engage the ends of the transverse arm for urging the feeding means longitudinally of said feed barrel, and rotary feed screws mounting the annular ring upon said base, said feed screws being in threaded engagement with said annular ring for movement thereof longitudinally of said feed barrel.

7. A contouring machine comprising a feed barrel having elongated slots extending substantially the length thereof, bearings rotatably mounting said feed barrel on said base, chuck jaws mounted in said feed barrel adapted to sfidably receive a blank stock therebetween, blank stock feeding means slidably mounted within said feed barrel, said feeding means comprising a pair of aligned rods mounted longitudinally within said feed barrel, a cross piece slidably mounted on said rods, a pushing pin pivotally mounted on said cross piece adapted to engage the blank stock and push the same through the chuck jaws as the feed barrel rotates, a transverse arm pivotally mounted on said cross piece, said transverse arm extending through the elongated slots in said feed barrel, an annular ring surrounding said feed barrel positioned to engage the ends of the transverse arm for urging the feeding means longitudinally of said feed barrel, rotary feed screws mounting the annular ring upon said base, said feed screws being in threaded engagement with said annular ring for movement thereof longitudinally of said feed barrel, means to rotatably mount a template on said base for rotation with said feed barrel, a torque shaft rotatably mounted on said base, a fol'ower for said template slidably mounted on said torque shaft, a feed screw threadably carried by said follower for longitudinal movement along said torque shaft, and driving means connected to the feed screws in engagement with the annular ring and with the feed screw carried by the follower for driving said screws in timed relation.

8. A contouring machine comprising a base, a rotary cutter, means to pivotally mount said outter on said base, means to rotatably mount a template on said base, a blank stock feed barrel, means to rotatably mount said feed barrel on said base and adapted to rotate with said template, said barrel having elongated slots therein, blank stock feeding means carried by said feed barrel, a pair of complementary chuck jaws mounted in said feed barrel adapted to slidably receive a blank stock therebetween, said feeding means comprising a pair of aligned rods mounted longitudinally within said feed barrel, a cross piece slidably mounted on said rods, a pushing pin pivotally mounted on said cross piece adapted to engage the blank stock and push the same through the chuck jaws as the feed barrel rotates,

a transverse arm pivotally mounted on said cross piece, said transverse arm extending through the elongated slots in said feed barrel, an annular ring surrounding said feed barrel positioned to 

